Resilient retention method

ABSTRACT

A resilient retention method which retains two assemblies axially through the use of a flange and lip arrangement and simultaneously retains those assemblies rotationally through either a radial detent or a snap spring are shown in variations. The designs are especially configured for molding so that each might utilize the material properties available and yet be economically manufactured. Further, user features including both visual and potentially audible indications of full assembly are incorporated into the designs and automatically achieved. Shut-off valve designs are shown which are automatically delayed in opening until some axial retention occurs to minimize any blow-off or other undesirable operational events. Swivel features may be incorporated when the application requires.

This application is a divisional application of Ser. No. 09/305,229,filed May 4, 1999, now U.S. Pat. No. 6,305,724, which is a divisionalapplication of application Ser. No. 08/806,391, filed Feb. 26, 1997, nowissued as U.S. Pat. No. 5,937,885, which in turn is a divisionalapplication of Ser. No. 08/463,692, filed Jun. 5, 1995, now issued asU.S. Pat. No. 5,799,987, each hereby incorporated by reference.

BACKGROUND OF THE INVENTION

This invention relates generally to fluid fittings. Specifically, itinvolves the field of molded coupling systems for quickly connecting anddisconnecting fittings which handle fluids. The invention presents anumber of compact designs which not only are economical to manufacture,but they also have a number of functional advantages. While especiallyadapted to accommodate the requirements of injection molded manufacture,the designs are suited to other types of manufacture as well.

The fluid fitting area is one which has existed for years. As moreeconomic products have been sought the desire to adapt designs forinjection molding has increased. In the majority of instances thisadaptation has occurred by merely molding existing designs. In onlylimited instances have those designing products sought to createcompletely new designs which are especially adapted to a moldingenvironment, that is, where a cavity shape is imparted to some type ofmaterial. One of the fields within this general area which has beenparticularly challenging to adapt for economical manufacture is that offluid fitting quick disconnects. Often due to this field's sometimesunusual material requirements, it has been perceived as requiring ahybrid approach. Through this approach, while some components have beenmolded, others have been machined or the like. Thus, rather than beingoptimized for economical manufacture such as is available in theinjection molding environment, designers often have accepted limitationsin either operation or manufacture.

Naturally, the problems designers have faced are greatly varied based inpart upon the application involved. In some applications, the physicalsize of the quick disconnect designs have been a challenge. In otherapplications, reliability and the actual operation of coupling the twoassemblies together has been the challenge. Other problems have rangedfrom challenges in achieving adequate locking of the coupling toproblems in creating shut-off valve subassemblies. Irrespective of thespecific operational problems deemed paramount, it has been almostuniversally true that existing designs have not been able to bemanufactured as economically as desired. In spite of a demand for highreliability and ease of use, consumers have been reluctant toincorporate components which cost many times the amount of a typicalfitting. The present invention presents quick disconnect designsintended to satisfy most if not all these desires. Importantly, it doesso through a design which was uniquely developed to utilize thestrengths and minimize the weaknesses involved in a molding environment.Perhaps most importantly from a commercial perspective, the design isone which can be manufactured at fractions of the cost of many existingdesigns.

As is often true for fluid fittings in general, many aspects of theinvention utilize elements which have long been available. In spite ofthis fact, and in spite of the fact that those skilled in the art ofmolded fluid fitting couplings had long desired such a design, theinvention applies these elements in a fashion which achieves long feltneeds very economically. Perhaps to some degree this may be due to thefact that prior to the teachings of this invention those skilled in thisfield may have been directed away from the utilization of a purelymolded quick disconnect design. Instead, it appears that those involvedin this field have tended to believe that it was necessary to pursuehybrid designs to achieve the desired results. The present inventionshows that such assumptions were, in fact, not true. To some extent theembodiments disclosed might even be viewed as presenting unexpectedresults in that they show that a completely molded design can achievemost (if not all) of the previously existing design requirements.

SUMMARY OF THE INVENTION

The present invention provides a quick disconnect fluid fitting couplingsystem which can not only be completely molded but which also canconsist of as little as two parts. In one embodiment, the designinvolves male and female assemblies which are held axially by a flangeand which lock in place through a radially resilient detent at theflange's outer abutment. Another embodiment includes a molded annularspring which locks the two assemblies together. A number of otherfeatures such as swivels and shut-off valves are also disclosed. All ofthese may be utilized independently or in conjunction with each other toachieve a very universal system.

As mentioned, it is an object of the invention to achieve a practicaldesign which properly balances the size, expense, and manufacturingneeds of users desiring a fluid fitting coupling system. In keeping withthis object, one of the goals is to provide a completely moldable designwhich not only is economical to assemble, but which is also easy tooperate. It is also a goal to provide a sufficiently strong designwithout compromise due to molding. Further, a goal is to allow for acompletely nonmetallic coupling system which can be used in thoseapplications having such demands.

Yet another object of the invention is to allow for a system whichsatisfies operational needs. Thus goals include providing a system whichis virtually foolproof in achieving a locked, coupled state, and whichis very difficult for operators to misuse. These goals are achieved, inpart, by providing for visual and possibly auditory indications oflocking. They are also achieved by providing designs which can beconfigured for use in any direction and for use with a minimum ofdifferent directional operations when appropriate.

Another broad object of the invention is to present a system with manydesign variations available to system designers. In meeting thedesigner's needs, it is a goal to provide a system of parts and featureswhich can be configured as appropriate to the specific application. Forsystems requiring a shut-off valve arrangement, the invention has as agoal, satisfying operator and safety needs by automatically achievingcoupling retention prior to any opening of the shut-off valves withinthe assemblies.

Naturally, further objects of the invention are disclosed throughoutother areas of the specification and claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an exploded perspective view of one embodiment.

FIG. 2 is an end view of the female part shown in FIG. 1.

FIG. 3 is a side view of the female assembly shown in FIGS. 1 and 2.

Figure 4 is a side cross sectional view of an assembled coupling asshown in FIG. 1.

FIG. 5 is an end cross sectional view of the assembled couplings asshown in FIG. 4.

FIG. 6 is an exploded perspective view of a spring-locked embodiment.

FIG. 7 is an end cross sectional view of the assembled couplings asshown in FIG. 6.

FIG. 8 is a side view of a male part of another spring-lockedembodiment.

FIG. 9 is a perspective view of the spring member design shown in FIG.8.

FIG. 10 is an exploded perspective view of an embodiment with aswiveling male part.

FIG. 11 is an exploded perspective view of another swiveling design.

FIG. 12 is an explode perspective view of an embodiment with dualshut-off valves.

FIG. 13 is a front view of a shut-off valve member.

FIG. 14 is a side view of the shut-off valve member shown in FIG. 13.

FIG. 15 is a side view of a shut-off valve spring member.

FIG. 16 is a perspective view of the radially helical surface as mightbe used in a shut-off valve.

FIG. 17 is an end view of a single shut-off valve embodiment.

FIG. 18 is a cross sectional view of the dual shut-off valve designshown in FIG. 13 prior to locking the coupling together.

FIG. 19 is a cross sectional view of the dual shut-off valve designshown in FIG. 13 after locking the coupling together.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

As can be seen from the drawings, the basic concepts of the presentinvention may be embodied in a number of different ways. FIG. 1 shows abasic coupling system according to the invention. In standard fashion,the system involves a first fluid fitting assembly (1) which is capableof being mated with and coupled to a second fluid fitting assembly (2).

As those involved in creating such coupling systems are well aware, itis generally desirable to have the maximum outer diameter of the systemas small as possible while having the largest possible maximum innerdiameter for the fluid to pass through. This is achieved to asignificant degree in the design shown in FIG. 1. As shown, the firstfluid fitting assembly (1) includes a first fluid fitting body (3) whichis positioned about a central axis (4) within a first fluid passageway(5). In order to provide coupling, the first fluid fitting assembly (1)is responsive to a first axial retainer (6). As with almost all fluidfittings, first fluid fitting assembly (1) includes a fitting section(15) which may be a threaded portion as shown or some other type offitting arrangement. The fitting section may be greatly varied, rangingfrom barb sections to luer arrangements and the like. Through suchdesigns, the fitting coupling system is designed to be able toaccommodate fluids, that is gasses (e.g., vacuum, pneumatics, etc.) orliquids (e.g., water, hydraulic fluid, etc.) which pass through or aremaintained by the fluid passageways.

As is easily appreciated, in order to create a coupling, the secondfluid fitting assembly (2) has a second fluid fitting body (7) withinwhich there is a second fluid passageway (8). Importantly, the secondfluid fitting body (7) is responsive to a second axial retainer (9)which is capable of engaging the first axial retainer (6). Once engaged,both the second fluid fitting assembly (2) and the first axial retainer(6) are then responsive to the second axial retainer (9). As may beunderstood from the arrangements shown, the term “responsive”encompasses a broad variety of interactions. In keeping with its broadmeaning, the term includes a mere result orientation. It encompasses allsituations where merely since one element is present, another elementdirectly or indirectly is affected somehow. Naturally, it also includesnarrower interpretations such as purely physical arrangements. Examplesof these would include the two elements being attached to each other,the two elements touching, or even them being unitary sections of anintegral component.

As shown in FIG. 1, both the first and second axial retainers involve acoordinated lip and flange design. For the first fluid fitting assembly(1) this is shown in FIG. 3 where it can be seen that the first fluidfitting body (3) has a lip support (10) to which is attached at leastone retaining lip (12). As is discussed later with respect torotationally retaining the coupled system, it should be understood thatthe lip support (10) has a lip support inner surface (11). Further, asshown it can be seen that the retaining lip (12) extends radially inwardtoward the central axis (4) from the lip support (10). As oneenhancement, the first fluid fitting body (1) has structure in betweenthe two lip supports (10). Unlike other designs by having thisstructure, the strength is enhanced and the entire area is surroundedand protected.

To mate with the first fluid fitting assembly (1), the second fluidfitting assembly (2) includes at least one flange (14) which is attachedto a flange support (13) and which is capable of engaging the retaininglip (12). There may, of course, be two diametrically opposed flanges asshown. As those skilled in this field understand, with the balancedarrangement of two flanges as shown, the pressure capability isenhanced. Naturally, other balancing designs are possible; all that isnecessary is that the flanges be equally spaced around the central axis(4). These types of designs not only afford better strength againstfailure, they also afford better sealing as there is less chance of aradial displacement of the seal. As those using an unbalancedarrangement have apparently not realized, through balancing the design,leakage is less likely. As shown, it also can be seen that the flanges(14) can extend radially outward beyond the flange supports (13) and canbe axially fixed with respect to the second fluid fitting body (7).Further, the entire part may be designed for uniform molding thicknessby including the relief areas shown.

To operate and couple this fluid fitting coupling system, it is onlynecessary to insert the first and second fluid fitting assemblies (1 and2). This insertion may cause the coupling seal (18) to seal one assemblyto the other. Next, the assemblies are axially engaged by rotating one(or a portion of one) with respect to the other (or a portion of theother) so that the flanges (14) slide under the retaining lips (12).This can be understood easier with reference to FIG. 2 where it can beunderstood that flanges (14) would initially fit within the flangerecesses (32). Then, through at least some rotation of one fitting bodywith respect to the other fitting body, the flanges (14) would berotated under the retaining lips (12) so that the first and second fluidassemblies (1 and 2) would be axially retained with respect to eachother.

As can be understood from FIG. 4, when assembled the coupling seal (18)is established between the first and second fluid fitting assemblies (1and 2). This coupling seal (18) may be simply an O-ring placed on secondfluid fitting assembly (2). Additionally, it should be understood that avariety of other types of coupling seals are possible including, but notlimited to, integral molded seals and the like. Further, coupling seal(18) may be entirely omitted. (It is expected, however, that in almostall fluid fitting applications it would be desirable to include sometype of coupling seal (18) even if such were merely a close fit betweenthe two assemblies. As may be appreciated, from FIG. 4, it can be seenthat the type of coupling seal (18) shown is subjected only to one levelof compression force during the assembly process. Unlike some otherdesigns, the coupling seal (18) is never over-compressed and thenrelaxed when achieving the locking of the disconnect system.

In addition, it is possible to have the system incorporate some type ofstops (20) which may limit the amount of rotation at a desired point.Naturally, such stops should be coordinated between the first and secondassembly parts. There may be a great variety of different designsincluding tabs, recesses and even nonsymmetrical designs to achieve thedesired end. A tab/recess arrangement is shown in FIGS. 1 and 2. Forbetter strength, these are designed to have a more nearly radial matingoccur at the point were it is desired to stop rotation. As is discussedlater, a nonsymmetrical design is shown in FIGS. 6 and 7. Regardless ofthe design chosen, the stops may serve to limit rotation to the degreedesired. Naturally, the stops may be entirely omitted. This may bedesirable in instances where constant rotation (to engage and disengage)is desired.

Whether stops (20) are included or not, it can be important to includesome type of rotational retainer. The rotational retainer wouldrotationally lock the first fluid fitting body (3) with respect to thesecond fluid fitting body (7) after they are fully engaged. It wouldlimit the ability of the two fitting bodies to rotate with respect toeach other. As perhaps best illustrated in FIG. 5, it can be understoodthat in the design shown, the rotational retainer may be achieved byproperly designing the shape of the inner surface (11) of the lipsupport (10) and the outer surface (28) of the flange (14). As shown inFIG. 5, it may be understood that both the inner surface (11) of the lipsupport (10) and the outer surface (28) of the flange (14) may haveplanar portions which are designed to abut when the system is fullyassembled. Regardless of the shape chosen, by purposefully avoiding aperfectly circular surface, the actual rotation of the two bodies withrespect to each other can cause the surfaces to radially compress andthen to relax as they lock in place. Further, since it is possible thatthe coupling system may be engaged for long periods of time, it may bedesirable to have little or no axial compression when the parts arefully engaged. Thus, the radial resilience may not tend to decay withtime in most applications.

As mentioned, the existence of compression creates the rotationallocking. Since the compression would not be reduced until after thedesigns were fully assembled with respect to each other, it would serveas one indication of full assembly. No radial compression could occur(or be felt) unless the two assemblies were properly inserted. As shown,it should be understood that the radial compression would thus limit therotation and would occur at the abutment (27) between the first andsecond fluid fitting assembly bodies (3 and 7).

Unlike other designs it can be understood that by using a radialresiliency to lock rotation, axial tension or forces play no part andare not necessary in order to accomplish retaining the two bodiesrotationally. This enhances the coupling seal (18) by not requiring itto be overcompressed as mentioned later. Further, by using the abutmentbetween the two pieces to achieve the lock, the design is somewhatfoolproof in that no locking can be felt or achieved until the parts arecorrectly engaged. For reliability, simplicity of design, andmanufacturing reasons, it is possible to use a design as shown where theabutment between the two pieces is not a separate flexing lockingmember. In keeping with the goal of providing easily variedconfigurations, this makes the system more universal. Such a design isalso particularly well suited to a molded system because the materialsused in molding can be somewhat resilient—and indeed may even be chosenfor this characteristic. By having resilient material, the radialcompression can form a radially resilient rotational lock at theabutment (27). Thus, the abutment (27) itself may create the radiallyresilient rotational lock.

As mentioned earlier, it is possible to have many different designs formthe radially resilient rotational lock. By using planar surfaces, arelatively simple and moldable design is achieved. As can be seen, theplanar portions are parallel to the central axis (4) and perpendicularfrom a line from the planar portion to the central axis. Other designsare possible ranging from separate elements to flexible arms totab/recess arrangements. All that may be necessary is that the surfacesbe noncircular and corresponding, that is, they coordinate with eachother to achieve the desired effect. For the design shown it is alsopossible to have the abutment between the inner surface of the retaininglip (12) and the outer surface of the flange support (13) beappropriately shaped. While this is an equivalent design, it may not,however, be as optimum as the design shown since such an abutment wouldbe closer to the central axis (4) and would thus present a lesser momentarm to restrain rotation.

Another feature of this design is the desirability of a system whichexternally can inform the operator when the assembly operation iscomplete. This is achieved through the shaping of the external nutdesign shown in FIG. 1. This nut design is shaped asymmetrically for anumber of reasons. First, when the asymmetric surfaces on the first andsecond assemblies are aligned, it can be seen that the designs areproperly rotated. As shown in the cross sections in FIGS. 2 and 5, thenut on each assembly body may include a corresponding first and secondpair of flat side sections (21) and (24). Especially for a two flangesdesign as shown, each of these pairs of flat side sections may beconfigured so that they diametrically oppose each other on each of theirrespective fluid fitting bodies. Further, they may be parallel to thecentral axis and, as with the abutment shown in FIG. 5, perpendicular toa line extending from the flat side sections through the central axis.When the flat side sections are aligned, the parts are correctlyassembled.

Second, the asymmetric design of the external nuts serves to addstrength. As shown in FIG. 5, when the flat side sections are configuredto be orthogonal to the planar sections forming the abutment (27), thethinner walls existing will not be in the area of maximum stress. Thisis because in between each of the first and second pairs of flat sidesections (21) and (24), may be corresponding pairs of toothed facesegments (23). As shown, these are diametrically opposed adjacent to theflat side sections. In order to include as much material as possible atthe most highly stressed area, namely, in the vicinity of the lipsupport (10), it may be desirable to provide five teeth (26) on each ofthe tooth faced segments and to radially align them with the innersurface (11) of the lip support (10). Perhaps surprisingly, this can addabout 60% to the pressure strength of the coupling. When the designs areunder pressure, since retaining lip (12) acts to axially retain flange(14), the forces will be spread over a larger area.

As yet another benefit, when each of the fluid fitting assemblies havethese nut designs, they may be assembled with either an open-end wrenchor a box wrench. Thus a box wrench (12 point) is accommodated by havingfive teeth in between each planar surface. Other designs are alsopossible, including, but not limited to two and three point designswhich would still fit a box wrench and the like. The enhanced grippingof such a design can be extremely important for a molded componentbecause not only is the material likely a plastic, but it also may havebeen specifically chosen to be flexible to accommodate the radialresiliency desired for the rotational lock discussed earlier. This nutdesign might even be considered an independent invention as it may haveapplication not only in other fields in the fluid fitting area, but alsoin other general areas such as the fastening area.

As shown in FIGS. 1 and 3, in order to facilitate molding at thelocation of the planar section on the inner surface (11) of the lipsupport (10), the design shown includes access entries (30) beneath theretaining lip (12) and adjacent the inner surface (11). Access entries(30) may serve to allow the mold to include inserts through the accessentry (30) to form the undercut necessary to create the lip (12). Forfurther efficiency, the inner surface (11) of the lip support (10) canbe planar throughout its entire length so that these inserts can beeasily pulled out with only one motion. Thus the piece can be made withless complicated molds. Naturally, the access entries (30) are notmandatory as other molding arrangements are possible.

Another unique embodiment of the invention is shown in FIG. 6. Asmentioned a host of different ways to lock the coupling against rotationare possible. This embodiment involves the use of a spring member (31)which has an integral rotational lock. Rather than being radiallyresilient, this rotational lock is essentially tabs (33) on the springmember (31) which are designed to fit within the flange recesses (32).Once the tabs (33) are positioned within the flange recesses (32), theflanges (14) will be prohibited from rotating. Thus the coupling will belocked together. Unrelated to this locking, it should be noted from FIG.6, that the first fluid fitting assembly (1) can be molded without theinclusion of any access entries.

FIG. 6 also shows that the spring number (31) can be rotationallyrestrained when assembled onto the second fluid fitting assembly (2). Inthe design shown this is accomplished in one way by a pair ofdiametrically opposed chord supports (39). The chord supports (39) bothsupport the tabs (33) and extend internally so as to fit withincorresponding chord recesses (34) on the second fluid fitting assembly(2). Through this arrangement, it can be understood that spring member(31) will not be permitted to rotate with respect to second fluidfitting body (7). Thus, when tabs (33) are inserted within the flangerecesses (32), the entire coupling will be held together. Naturally, itshould be understood that a host of different designs are possible inorder to limit rotation. Each should be considered an equivalent as thebroad conceptual goal is all that needs to be met. Through the design ofthe chord support (39) it also is impossible to assemble the springmember (31) backwards. It should also be understood that through properdesign it is also possible to provide rotational locking without havingthe spring memeber (31) locked to the second fluid fitting assembly (2).One possibility would be to lengthen the tabs (33) so that they couldextend beyond the lip and thus engage the flanges (14). This mightrequire more spring travel.

The operation of the design shown in FIG. 6 is fairly simple. First, thefirst and second fluid fitting assemblies were axially aligned andinserted so that flanges (14) sit within the corresponding portions ofthe first fluid fitting assembly (1). This axial insertion compressesthe spring member (31). By rotating one fluid fitting assembly withrespect to the other, the flanges (14) are axially retained when theyslide underneath the retaining lips (12) as discussed earlier. When theflanges are fully rotated, tabs (33) will align with the flange recesses(32) and the decompressing of the spring member (31) will cause the tabs(33) to snap into the flange recesses (32). This will effectively lockthe device together.

As an enhancement to the durability of this design, it may also bedesirable that when tabs (33) snap into a recess such as the flangerecesses (32), the spring member (31) is no longer compressed. Since thecompression of the spring member serves no purpose other than merelyholding the tabs (33) in place, the lack of compression will notadversely affect its rotational locking function. Thus, by completelyrelaxing spring member (31), it will not be subjected to continuouscompression and thus will not tend to lose its full amount of originalresiliency. To disassemble the coupling, the spring member (31) needonly be compressed by gripping the outer end portion surface (38), andsliding it axially so as to compress the spring segment (37) and thusremove tabs (33) from flange recesses (32). To facilitate this gripping,the outer end portion surface (38) may be textured. Then the twoassemblies may be rotated and axially separated.

The design shown on FIG. 6 also includes a number of enhancements.First, spring member (31) is cylindrical so that it surrounds a portionof the second fluid fitting assembly (2). This is stronger, minimizesthe exposure to wear, and also serves to protect the fitting assembly.The integral rotational lock is shown as positioned on an annular endportion (35) of the spring member (31). By placing tabs (33) on theannular end portion (35) so that they project off of the annular endportion but do not fully extend to the outer edge of the annular edgeportion, tabs (33) are likewise protected by the outer end portion (38)of the spring member (31). This also allows the sections in between theretaining lips to be included as mentioned earlier.

At the other end of the spring member (31) is a cylindrical springsegment (37). This segment is designed in a manner so as to be easilymolded. In keeping with the goal of providing an easily andinexpensively manufactured item, it can be seen that the individualspring members (31) may be a single molded unitary design. This affordsthe economic advantages mentioned earlier while simultaneously achievinga rotational lock which is disposed between the first and second fluidfitting assemblies (1 and 2).

An alternative design for a unitary spring member is shown in FIGS. 8and 9. In this unitary molded design, it can be seen that one endportion may include a catch (40) which may serve to interact with otherportions of second fluid fitting assembly body (7) to hold the springmember (31) onto the second fluid fitting assembly body (7). Again, thisdesign may be easily molded by making the catch (40) a flexible portionwhich would snap over some annular ring or the like on an inner portionof the second fluid fitting assembly (2). By placing the catch (40) onthe end of the spring member (31) which is away from the spring, thedesign may achieve a goal of limiting the extensibility of the spring soas to prevent over-extension.

To illustrate another alternative, the embodiment shown in FIG. 6 isshown including a different flange design. As shown in FIGS. 6 and 7,this flange design is noncircular, not for rotational locking, but inorder to stop rotation at the desired point as mentioned earlier. Sincethe spring member (31) will serve to achieve the rotational lockingfunction, rotational locking through the action of the abutment betweenflange (14) and the first fluid fitting assembly (1) is unnecessary.Rather, the asymmetry of the flanges (14) shown serves to stop rotationat the proper spot. FIG. 7 shows a cross section view of such flanges asthey might be positioned when fully assembled. As can be appreciated,the shape of the flange prevents further rotation in the directionshown. Naturally, such a design might be incorporated in otherembodiments and might even be incorporated in the embodiment includingthe resilient radial detent mentioned earlier.

As yet another enhancement to the coupling system described, all of thedesigns mentioned may include a swivel feature. As shown in FIG. 10,this can be accomplished through the use of a stem (41) which isdesigned to be rotatably positioned within a central cavity of one ofthe fluid fitting assembly bodies such as an assembly body externallysimilar to second fluid fitting assembly body (7). By establishing thestem (41) so as to rotate freely within the second fluid fittingassembly body (7), any hose or other fluid handling system may beallowed to rotate and not kink or otherwise negatively impact the sealsmaintained. This may be very important for a design such as that shownin FIG. 1 where rotation could unlock the coupling.

Importantly, the stem (41) must be axially retained with respect to thesecond fluid fitting assembly body (7). This can be accomplished throughflexible projections (46) which would serve to snap over the stem (41)and retain it axially within the body. When fitting the stem (41) withinthe central cavity (42) of the second fluid fitting assembly body (7),it will be appreciated that it may be important to create a seal betweenthe stem (41) and the fluid fitting assembly. This may be accomplishedby a stem O-ring (43) which would be free to rotate and slide within theassembly while maintaining its seal.

As shown, stem (41) may be molded in a fashion which includes moldingrecesses to allow even thickness or mold gate vestage as those skilledin the molding field would well appreciate. Similarly, stem (41) mayinclude a fitting end (45) integral to it to allow connection to fluidsources, or otherwise. Naturally, the swiveling component may bedesigned into either the male or female assembly.

The use of internal flexible projections (46) is but one technique forretaining stem (41) within its corresponding fluid fitting assemblybody. A host of other designs are also possible as those skilled in theart would readily understand. As shown in FIG. 11, one of the many otheralternatives available would be the inclusion of an assembled bodyaround stem (41). This assembled body might be made of two semicircularbody halves (49) which would be assembled around the stem (41). In thedesign shown, the body halves (49) may include some type of a retainerelement (52) to hold them together. They may also include guiding pins(50) and corresponding holes. The retainer elements (52) shown wouldhold the body halves (49) together through their barb design. As shown,the retainer elements (52) might be positioned on an end opposite theinserted end which has on it flanges (14) so that when the coupling wasfully assembled, flanges (14) would be held together by the femaleportion and thus reduce the amount of stress which the retainer elements(52) would need to support (if any). Further, on designs which utilizethe unique nut shape mentioned earlier, it may be possible and desirableto position the end of the retainer elements (52) at the bottom (48) ofa tooth (26). In this fashion, it is less likely that such elements (52)would be exposed or subjected to forces which might cause it todisengage.

As mentioned earlier, it is often desirable for coupling systems toinclude shut-off valves so that they automatically seal when disengaged.In such systems, the valve is normally closed and is held open only bysome force other than the fluid pressure. Some of the possible shut-offvalve designs are shown in the figures. Referring to FIGS. 12 through19, it can be seen how a double shut-off valve design, that is, one inwhich each fitting assembly has its own shut-off valve may be achieved.As shown, both the first and second fluid fitting assemblies (1 and 2)include an axially moveable valve (55). This axially moveable valve (55)is responsive to rotation through an annular angled surface (59) whichis angled with respect to a plane perpendicular to the central axis.When such a valve is designed to be responsive to rotation, it is likelyimportant to include a rotational guide (56) which rotationallyrestrains the axially moveable valve (55) so that the rotation is forcedto cause axial movement and thus to open the valve. A valuable featureof the design shown is the fact that the system shown may be designed sothat before any opening of either axially moveable valve (55) occurs,the first and second fluid fitting assembly may be axially retained withrespect to each other. This can be accomplished by allowing the initialportion of rotation to cause the flanges (14) to become slightlypositioned underneath lip (12) prior to any engagement of the axiallymoveable valves (55).

To assemble this design the initial insertion causes the coupling seal(18) to be established between the first and second fluid fittingassemblies. After this has been accomplished the axially moveable valves(55) can open with no fluid flow outside of the coupling assembly. Oncethe flanges (14) are positioned under the lips (12) the assemblies areat least temporarily axially restrained. As further rotation continues,this rotation will now cause the shut-off valves to begin to open whilesimultaneously causing the flanges (14) to further be positionedunderneath the lips (12). In this fashion, the present design avoids anyrisk of blow-off and thus the pressure of the fluid will be less likelyto cause premature separation of the two fluid fitting assemblies beforethey have been fully engaged. This is naturally true regardless ofwhether there is one or two shut-off valves. When there are two shut-offvalves, however, the lower pressure of the exit side will likely causeit to open first. Thus, when the pressure side begins to open an exit isalready established thus even further lowering the resistance and riskof blow-off. This also has the benefit of allowing greater axialretention to occur when the higher pressure is released.

As may be appreciated, the shut-off valves may operate in somewhattraditional fashion with respect to their sealing. This might beaccomplished through the use of shut-off valve seals (51) which areresponsive to an axially moveable valve support (54) to which isattached the annular angled surface (59). By also including a valvespring member (57), the axially moveable valve (55) will be yieldablyurged into the closed position. In a potential departure from one of thegoals of the invention, it might be understood that valve spring member(57) while capable of being molded, might be selected to be a metallicspring. This for the simple reason that since the majority of the usewould have the shut-off valve be open, a plastic spring may loose itsresiliency whereas a metal spring might retain it. Naturally, as bettermaterials are discovered or tested, this might prove to be unnecessaryand an entirely molded design might be as reliable.

The integral spring design shown also can minimize assembly andmanufacture requirements. Such a spring simply need be inserted over thevalve support (54) and then the shut-off valve seal (51) can be insertedto hold it in place. Importantly, once the valve spring member (57)urges the shut-off valve seal (51) to a closed position, a fluidpassageway seal would be created so that no fluid could flow. Further,the pressure of the fluid would serve to enhance the seal as would bereadily understood.

As mentioned earlier, single or double shut-off valve designs can beaccomplished. In a single shut-off valve design, it might be understoodthat a rotationally fixed slide (60) might be included. This is shown inFIG. 17. This rotationally fixed slide (60) would serve to engage theannular angled surface (59) on the only shut-off valve in the system andthus open it at the appropriate time. As those skilled in the art wouldreadily appreciate, this rotationally fixed slide might have a host ofdifferent designs from bars to tabs and other types of designs. It maybe separate or integral to the other fitting assembly, as well.

FIG. 16 shows the nature of the annular angled surface (59) as optimallydesigned for either a single or double shut-off valve system. As thisfigure shows, the annular angled surface may be a radially helicalsurface so that throughout rotation maximum contact is achieved. Thiswill minimize wear. The radially helical surface is angled with respectto a plane perpendicular to the central axis to achieve the axialmovement desired. Naturally, other surface shapes are possible as well.As also shown in each of the shut-off valve figures, the double shut-offvalve design may include two pairs of surfaces. This might allowrotation in either direction. Naturally, a single surface would beappropriate for designs which include the stops (20) mentioned earlieras two-way rotation would not be possible in such designs.

Referring to FIGS. 18 and 19, it may be understood how yet anotherfeature of a double shut-off valve design might be accomplished. Asmentioned earlier, the shut-off valves may not simultaneously open. Inorder to assure that they both do fully open, each shut-off valve mayinclude a corresponding valve stop (63). This valve stop may limit theaxial movement response of each shut-off valve so that when one is fullyopened, it is restrained, and thus the other must open to its fullamount. As shown, valve stop (63) can be achieved in conjunction withthe rotational guide (56) by merely ending the recess within whichsliding may occur. Naturally, other designs are possible as well, butimportantly, the use of a stop will force the other fluid fittingpassageway seal to open an equal amount. This stop could also be thecompression of the valve spring member (57) to its solid height.

In addition, in FIG. 18 it can be seen how the design can accomplish thedelay in opening the valve. As shown, the two annular angled surfaces(59) do not initially engage each other. Instead a gap (65) is formed.Only after some rotation of the two bodies—and thus some axialretention—do the two surfaces engage each other causing axial motionopening the two valves.

Also, as a comparison of FIGS. 18 and 19 would highlight and asmentioned earlier, it is possible to either include or not include theaccess entries. They are not shown on the first fluid fitting assembly(1) of FIG. 18, but are shown in its corresponsing part in FIG. 19 toillustrate this aspect. Nuts could also be included on such designs butare not shown on either of these two figures. In addition, through thedesigns shown in FIGS. 18 and 19 it can be understood how a shut-offvalve component can be an important part of the system presented. Asshown, either part can be designed to include retaining lips (12) onboth ends so that they may be used as a spliced insert to place ashut-off valve in the system.

The foregoing discussion and the claims which follow describe thepreferred embodiments of the present invention. Particularly withrespect to the claims, it should be understood that changes may be madewithout departing from their essence. In this regard it is intended thatsuch changes would still fall within the scope of the present invention.It is simply not practical to describe and claim all possible revisionsto present invention. To the extent such revisions utilize the essenceof any feature of the invention, each would naturally fall within thebreadth of protection encompassed by this patent. It is also true thatvarious permutations and combinations might be achieved. Again, each ofthese permutations and combinations should be encompassed by thispatent.

I claim:
 1. A method of coupling fluid fitting assemblies togethercomprising the steps of: a. axially engaging a first fluid fittingassembly having a first fluid fitting body, a central axis, and a firstfluid passageway and a second fluid fitting assembly having a secondfluid fitting body, a central axis, and a second fluid passageway; b.compressing a spring member disposed between said first and second fluidfitting assemblies; c. rotating said first fluid fitting body withrespect to said second fluid fitting body; d. axially retaining saidfirst fluid fitting assembly with respect to said second fluid fittingassembly; e. decompressing said spring member; and f. rotationallyretaining said first fluid fitting body with respect to said secondfluid fitting body through action of said spring member wherein saidstep of rotating said first fluid fitting body starts after the start ofsaid step of compressing said spring member.
 2. A method of couplingfluid fitting assemblies together as described in claim 1 wherein saidstep of compressing said spring member comprises the step of axiallycompressing said spring member.
 3. A method of coupling fluid fittingassemblies together as described in claim 2 and further comprising thestep of completely relaxing said spring member.
 4. A method of couplingfluid fitting assemblies together as described in claim 2 wherein saidstep of axially engaging said first fluid fitting assembly and saidsecond fluid fitting assembly comprises the step of inserting a flangeinto a flange recess and wherein said step of rotationally retainingsaid first fluid fitting body with respect to said second fluid fittingbody comprises the step of inserting a restraining tab into said flangerecess.
 5. A method of coupling fluid fitting assemblies together asdescribed in claim 1 further comprising the steps of: a. freely allowingrotation of a stem with respect to at least one of said fluid fittingassemblies when accomplishing said step of rotating said first fluidfitting body with respect to said second fluid fitting body; b. axiallyretaining said stem with respect to the fluid fitting body surroundingit; and c. sealing said stem to said other fluid fitting assembly.
 6. Amethod of coupling fluid fitting assemblies together as described inclaim 5 further comprising establishing a pair of generallysemi-circular body halves around said stem.
 7. A method of couplingfluid fitting assemblies together as described in claim 6 wherein saidaxially retaining said stem with respect to the fluid fitting bodysurrounding it further comprises rotatably engaging said pair ofgenerally semi-circular body halves around said stem with said stemretaining element.